Automatic transmission



M r h 23, 1954 A. P. SCHNEIDER AUTOMATIC TRANSMISSION Patented Mar. 23, 1954 UNITED sures Parent QeFFlCE 2,672,767 AUTOMATIC TRANSMISSION. Albert P: schneider Milwaukee; Wis; AsPPliQa tiQ IQQtObGI' 11, lfififlrseri l -N0-.-18 5 34 Claims.

This. invention relates to improvements in automatie transmissions. and more. particularly Modemautomobiles are equipped with various types-or automatic fiuid transmissions. some of such; transmissions embody means forlocking together thedrivingand driven elements of the fluid coupling when the automobile reaches a oertain speed. This is effectiv to increase the efficiency of thefiuid transmission by eliminating entirely allelippage in'the coupling when the elements thereof arelocked together.

this locking device responsive entirely to the speedoithe automobile is not entirely satisthe fluid coupling eleobjectionable jerking action.

With the above in mind, it is a general object of the present invention to provide an improved automatic transmission in which the incidence of slippage is greatly reduced and in which excessive slippage is substantiallyentirely prevented, thereby attaining withconventional fluid transmissions.

A further object of the invention is to provide hicle.

A further objectyof the an improved automatic transmission of the type is impossible to effect a an efficiency not possible invention is to provide lit.

driven by ,the driving asl ghtly larger positive displacementpump connectedin series with the first mentioned pump and driven .by the driven element of the coupling, the element locking mechanism communicating connecting. said pumps, whereby driven element at a predetermined speed relative to thedriving lementv creates a fluid pressure condition in the line connecting said"pumps andcauses actuation of the element locking mechanism.

A further specific. object of the invention is to provide an automatic with the. line rotation of the WhempaSflng. or when goingup asteep hill.

With the aboveand other ,objects intview', the invention consists of the improved automatic transmission and all of its parts and combinations, as set forth in the claims, and all equivalents thereof.

In the drawing accompanying and forming a part of this specification, wherein is shown one complete embodiment of the preferred form of the invention, and wherein like characters of reference indicate the same parts in all of the views:

Fig. 1 is a schematic fragmentary sectional plan view of the improved transmission; and

Fig. 2 is a transverse vertical sectional view of the planetary gear set and one of its train engaging mechanisms taken approximately along the line 22 of Fig. 1.

Referring more particularly to the drawing which illustrates the invention applied to a transmission having embodied therein an hydraulic fluid coupling and a planetary gear set, the numeral indicates a drive shaft which may be connected to a prime mover such as the internal combustion engine of an automobile. Attached to the drive shaft 5 is a housing 6 which is secured to the driving element 1 of a fluid coupling 4. Within the housing 6 is an annular cylinder 8 in which is mounted an annular piston c which is axially slidable and non-rotatable relative to the cylinder 8. An annular pressure transmitting member ill forms a part of the piston 9. tends radially inwardly from the periphery of the housing 6 and is spaced from the pressure transmitting member l3. An intermediate shaft i2 is positioned coaxial with the drive shaft 5 and has one end journalled in an axial recess l3 formed on the inner surface of the housing 6. The shaft l2 extends axially through the fluid coupling 4, and exteriorly of the coupling 4 the other end of said shaft forms the driving member of a planetary gear set l4. An annular friction plate [5 is fixed to the shaft l2 within the housing 5 and is positioned in the space between the flange H and the member Hi. The driven element lb of the fluid coupling 4 is also fixed to the shaft i2. It is apparent that when the piston 9 is moved to the right, as viewed in Fig. 1, the friction plate I5 is locked between the member I3 and the flange l l, thereby locking the driving element 1 of the coupling 4 to the driven element I6 thereof.

The planetary gear set M is preferably of the type having four forward speeds and a reverse. The gear set M has a casing l1 provided at its forward (left hand in Fig. 1) end with a bearing boss I8 through which the shaft l2 rotatably extends. The forward end of the bearing boss I3 is provided with an enlarged axial recess l9 which is adapted to accommodate a roller type one-way brake formed by earns formed on the shaft l2 and rollers 2| cooperating therewith. Within the casing H the shaft I2 is formed with a housing 22 which is similar to the housing 6. The housing 22 is provided with an annular piston 23 and an annular inwardly extending flange 24 similar to the piston and flange 3 and H respectively. A duct 25 communicates between the cylinder of the housing 22 and an annular oil groove 26 formed on the shaft l2 within the bearing boss It. An oil passage 21 extends through the bearing boss l8 and communicates between the groove 26 and the exterior of said boss.

A clutch and brake wheel 23 is freely rotatably mounted on the shaft l2 rearwardly of the housing 22, said wheel having a hub 23 and a periph- An annular flange H exeral rim 30. A friction plate 3| is fixed to the hub 29 and is positioned between the piston 23 and the flange 24 of the housing 22. It is apparent that when the piston 23 is moved toward the right, as viewed in Fig. l, the friction plate 3| is locked between the piston 23 and the flange 24, and the shaft I2 is thereby locked to the wheel 28. The mechanism for hydraulically actuating the piston 23 to accomplish the abovementioned locking action will be described hereinafter. A brake band 32 encircles the rim 33 of the wheel 23 within the casing H. The hub 29 is formed with external gear teeth at its right hand end.

A ring gear 33 is freely rotatably mounted on the shaft l2 and rotatably carries a plurality of planet pinions 34 which mesh with the gear teeth formed on the hub 29. A brake band 35 encircles the periphery of the ring gear 33 within the casing At its right hand end the shaft l2 is formed with a pair of spaced sun gears 36 and 31. A driven shaft 38 has one end rotatably extending through a suitable bearing in the rear end wall of the casing l'i coaxial with the shaft l2. Within the casing If the driven shaft 38 is formed with a pair of spaced carriers 39 and 40 which respectively carry a plurality of rotatable planet pinions 4| and 42. The planet pinions 4| mesh with the sun gear 31, as shown.

double ring gear member 43 is provided with a hub 44 which is rotatable on the driven shaft 33, said hub being formed with external gear teeth which mesh with the pinions 42. The double ring gear member 43 meshes with the pinions 4| and 34, as shown, and also serves as a carrier for a p'urality of planet pinions 45 which mesh with the ring gear 33 and with the sun gear 38. A brake band 46 encircles a peripheral portion of the double ring gear member 43 within the casing I! as shown. A ring gear ft! is freely rotatable on the driven shaft 38 and meshes with the planet pinions 42, as shown. The ring gear 41 is also provided with a brake band 48 which encircles the periphery thereof within the casing II.

In the preferred form of the invention each of the brake bands 32, 35, 46 and 48 is provided with a hydraulic piston band actuating mechanism. Fig. 2 shows one form of brake band actuating mechanism which may be used. In this form the casing ll is formed with a cylinder 49 in which a piston 53 is reciprocatable. The piston 53 has a pivotal connection, as at 5|, to the end of a bell crank lever 52 which is pivoted at 53 and is pivotally connected at 5!! to a link 55 which is adjustably connected to the movable end 56 of the brake band 43. The other end 57 of the brake band is fixed to the housing If, and a coiled compression spring 53, acting between the ends 55 and 51, serves to normally urge them apart to prevent drag on the gear 41. A passage 59 communicates between the closed end of the piston 49 and a conduit 63. I

Conduits 6!, E2 and 53 communicate with the cylinders of the actuating mechanisms (not shown) for the brake bands 32, 35 and 45 respectively.

In the gear set It the low forward speed is obtained by holding the ring gear 43 by means of the brake band 45. Power is then transmitted through the planetary gears 4|. To obtain the second speed, the brake band 45 is released and the ring gear 33 is held by means of the brake band 35. Power is then transmitted through the pinions 4| and 45. For the third speed, ring --"an external conduit -63.

gear 13 which drives a wheel of the pump "conduit "8 I.

pressure in said line exceeds j'theoutiet of the pre u reli and-the humeral I s ame? fr ea is reieased and 'the hiutch when 28 us -32. Poweristhe'ntrahsted' by the piliib'r'ls afi, 45 and 411. high eeapwhich isga y reIeasihg-tlie "brake s zt h -The fourth, diret drivefiis obtained and-fl on the wheel 28 plate 3I -betwee'n -the '{fiange =24. @his locks the entire forward speed po'r-tion or the assemmy together 'and causes it to rotate a's' a unit. '-To obtaih-'=1=eve'r se -rotation' of'the dr-iven shaft '30, the ring gear 41 is held against rotation hy means 0f the brake band '43.

The=drive shaft 5 is rotatabl y supportedin=a bearing 54, and said drive -*shaft is formed With it an annular oil groove 55 An oilipassagetfi communicatesbetween-the anmular cylinder 8 and the oil: groove 65, as shown.

A passage 6'! extends through the-bearing +96 andmdmmuniczttes between the oil groove 65 I and Keyed to i the drive "shaft 5 is a worm 'gear I59 which drives a wheel 10 meshed therewith, and 'said wheel in turn drives a shaft 1! and a positive displacement :pump =72.

-Keyed to the intermediate shaft 14 meshed therewith, and the wheel 74 "in turn,-drives ashaft -15and; a positive displacement pump it. Freely rotatably mountedon'theshaft I2 is-a worm I? *which is driven by-the-housing fi and drivingly {meshes with a wheel it. The wheel '18 in-turn drives a shaft 19 and -a positive displacement rum The pumps 16 and 00 may be of the same size, and the pump 72- is preferably of apredetermined smaller size than the pump T16, for example, the lpumpf'lZ may'have a capacity of approximately f8 5% ofthato"f thepump 16 for the same speeds. A conduit? I communicates between-the outlet The conduit 68 i'nturn communicates with the A conduit 82 communicates betfweh"the outlet of thepun 'ip 8'0 and the inlet fof'thepuhip 'IB, and a coriduit'83 corrimunicates "between a. sump 84 containing hydraulic fluid the irilet'ofthe'pun ip 80. jA conduit "85 communicates bet'ween'the conduit 'BJ I ,"afpressure relief valve8 6, anir-ilt check "valve 81 "and "a normally "open bleeder valve "of predetermined restricted Capacity "38. A c'onidliit 89 "communicates with the cipposite side of fthe valves '31 and. as and with the sump '84. A conduit 90 communicates between 'the fhonduit w ahda pressure relief va1ve9I and an f i 'ilet check valve 92. The other side of the valves "9! anu az communicatewith the conduit 89 leadin'gfto the -sump '84. A conduit 93 is connected to the" outlet of the 'pump12. "A pressure relief "valve94 communicates with the conduit 93 and "is preferably set to bleed the line 93 when the "approximately 80 unicates between ef valve 94 and a p'ressure relief valve 96 which is set to bleed the condii'it 95 when the pressure therein exceeds approximately pounds. "A branch conduit 9'I corrim-unicateswith the conduit-J95 and may s'upp'o'fin'ds. "A conduit 95 com" T11 ply fluid fora-11y desired auxiliary purposes-such 'a s lubrication "and the -1ike.

Theoutletof the valve 96 is connecte'd to a"conduit 90 Which, in =turn, communicates with a conduit '99 leading to the sump84.

The'num'eral I 00 indicates the accelerator 0f the "vehicle in which the invention I is 1 embodied, I indicates a normally cld'sed within said bearing.

I2 is -a worm have hat-mesh '-"axiall y inov'ahle stem I 0-2 'ififo- "j'ectin'g tlirough the floor bbard 103 ih aptisitibn tobe depressed by the accelerator *Whe n the datter is pushed-all the Way 'doW-h. The valvefml may have a cylindrical casing formed withdiametricallyopposedinlet and outletp'assages I04 and -I05 respectively. axially mo-valdle cylindrical valve meniber I06 is positioned ih 'the body of -the valve and-is formed with a diametrically extending bore l 0! ii-spring I08--urges thev'alve i'ne'inber iip'wardly to I the -positidn shown ;=*wherein 'thepaSsage I 01= is out of communication 'with the inlet {and Outlet ports I04 "and 105, and said valve is therebyclosed. Upon depression t the -stem 10'2, however, the valve'membe'r IOBis oved downwardlyagains't the compressionof the spring I08 "to --bririg the passage I01 into registration with the ports I0 and l05, thereby opening the valve. conduit I 09 I communicates betvve'en' the -'cdnduit andthe inlet port I04 of the v-lve I-0I. -A conduit I='I0 communicates-betweenthe -conduit 98 and the" outlet port I05 of-thevalve IOI.

-A distribution 'valve II I I has-an longdtedtuhular i cylindrical 1 body -I' I2 which may have one en d closed by athreaded cap I-I"3,and its-op'posite end is closed by a threadedfiplug 'I M. "The body t I2 has an elongated--axia1 bore I I 5-extending the maj or portion of *the length there'df and at the end adjacent "the -'cap H-"3 saidbody is formed with a bore poi tion I'I'fi ar increased diameter thereby forming a s'houlder -I"I "l. A sleeve valve II8 is axially slidable in 'the bore portion I It and is provided with an axiallyek H9. A tubular eittentending open ended bore sion I20=is formed on the end of 'the sleeve II 8 adjacent the cap H3, ancl'surroundingthe exten ion E20 there is a helicalc'ompression spring I 2 I having one end in abutment Withthe= cap I I3 and the other end in abutmerlt with the sleeve valve '8. The-spring-IL I normally-urges the sleeve valve H8 tovvard the-shoulder II'I which forms a-lim'it seat therefor.

The sleeve valve I I 8 is formed "with'a pairof spaced circumferential grooves I22 and-I23. The body I I2 is-formed with I ee -pair of spacewports 121i and I25Which communieate-withthegroove I22 whe'n the sleeve valveI I 8 is in the*positibn of Fig. 1. l-he-body H2 is also fcrmed with a pair of 7 ports I2t and I21which communicate with the groove 5Z2 whenthesleeve valve H8 is in abutment with the shoulder III the-boiiy I'I2 also-being-forined with ports l28 an'd I29 which communicate with the groove I23"tvhen the sleeve valve H8 is "in abutment withthe shoulder II'I. H a

A co'nduit l I 30 communicates at' one end with the passage?! in -the-bear'ing I8 of the planetary gear set I4 and communicates at its otherend with the ports I24 'and I26. The-conduit "85 communicates with the IJOItIZ8; andtheconduit '90 communioates with the ports-l 2 1 and {129. The" cap II3 of thevalvelll isform'ed Witha central aperture MI, and 'a c'ohduit l32 'coinmunicates between the aperture I 3 I -and=the'-con- V 3 communicates between the port I25"and theconduit 93.

'Axially slidably mounted'in thebore I I 51 of the valve body I I2 is a tubularcylindrical sh'uttle valve member I34 havinge its end adjadeiit-the sleeve I I8 open and ha"'ing its opp'osite end closed. A coiled compression spring' l35is"positioned in the bore-'I I5 and has oneend in envalve member I34. The valve member I34 may be formed with a projection I36 which is en- .gageable with the plug II4 to limit the movement of said member to the right, as viewed in Fig. 1.

The valve body H2 is formed with preferably four equally spaced ports I31, I38, I39 and I40. The valve body H2 is also formed with ports I45 and I46 which are preferably diametrically opposite the ports I38 and I39 respectively. The shuttle valve member I34 is formed adjacent one end with a port MI in its side wall, said port registering with the port I31 when the valve member I34 is in the position of Fig. l. The shuttle valve member I34 is also preferably formed with two circumferential grooves I42 and I43. The port MI and the grooves I42 and I43 may be spaced apart the same distance as the ports I31, I38, I39 and I40, and said grooves I42 and I43 may be connected by a longitudinal groove 205, which is positioned in longitudinal alignment with the ports I31, I38, I39 and I48, and by a longitudinal groove 286 which is positioned in longitudinal alignment with the ports I45 and I46. The body I I2 is also preferably formed with a port I41 adjacent the plug H4. The conduit 99 connects the ports I45, I46 and I41 to the sump 84.

Preferably formed on the valve body II2 adjacent the port I38 is a tubular auxiliary valve body I43 having an axial bore I49 and having a bore portion of enlarged diameter I58 communicating with the port I36. An elongated valve member II is positioned in the bore I49 and has formed on one end thereof a piston I52 which is axially slidable in the bore portion I58.

The outer end of the valve body I48 may be closed by a screw plug I53, and a compression spring I53 is positioned in the bore I49 between the plug I53 and the adjacent end of the valve member I5I. The valve member I5I is formed with a peripheral groove I54, and the body I48 is formed with a pair of spaced ports I55 and I 58 which register with the groove I54 when the valve member I5I is in the position of Fig. 1.

The valve body I48 is also formed with a pair of spaced ports I51 and I58 which are positioned to register with the groove I54 when the valve member is in its outermost position (not shown). The valve member I5I is also formed with a circumferential groove I59 spaced axially outwardly from the groove I54 and the ports I51 and I58.

Formed on the auxiliary valve body I48 adjacent its outer end is a cylindrical tubular extension I68 which projects at preferably a right I angle to the axis or" the bore I49 of said body. The extension I68 is formed with a cylindrical bore portion I6I adjacent the valve body I43 and is formed with a cylindrical bore portion I62 of larger diameter, outwardly of the bore portion I6I. A screw plug I63 is threaded into the outer end of the bore portion I6I, and a screw plug I64 is threaded into the outer end of the bore portion I62. An axially slidable piston rod I65 projects through a suitable axial aperture in the plug I63 and through a coaxial bore in the valve body I48. Fixed to the outer end of the piston rod I65 is a piston I66 which is axially slidable in the bore portion I62, and piston I61 is fixed to said piston rod and is axially slidable in the bore portion I6 I A coiled compression spring I68 is positioned in the bore I6I between the plug I63 and the piston I61, the spring I68 normally urging the piston I61 toward the right (see Fig. 1) to urge the rod I65 into engagement with the valve member I5I. The peripheral groove I59 of the valve member I5I is positioned so that when said valve member is in its outermost position (not shown) the end of the piston rod I65 will snap into said groove, under the urging of the spring I68, and will lock the valve member I5I in this position. The extension I5I) is formed with a port I69 communicating with the bore portion I6I at the inner side of the piston I61, and said extension is also formed with a port I18 communicating with the bore portion I62 adjacent the plug I63 at the inner side of the piston I66. The valve body I48 is also preferably formed with a passage III communicating with the enlarged bore I58 at its inner end, said passage being closed ofi by the piston I52 when said piston is in the position of Fig. 1.

A conduit I12 communicates between the port I and the conduit 98, and a check valve I13 is connected between the conduit I12 and the passage III. A check valve I14 is connected between the conduit I'I2 and the port I31, and a conduit I15 communicates between the port I51 and the conduit 93. A conduit I16 communicates between the port I69 in the tubular extension 268 and the conduit I38.

A valve body I11 which is preferably identical in all respects with the valve body I48 and which contains identical mechanism, is preferably formed on the valve body II2 adjacent the port I39 as shown. The valve body IE1 is formed with ports I18, I19, I88 and I8I corresponding to ports I51, I55, I58 and I56 respectively. The tubular extension of the valve body I11 is formed with ports I82 and I33 which correspond with the ports I18 and I59 respectively. A passage I84 of the valve body I11 corresponds with the passage I1I of the valve body I48.

A third valve I85 is formed on the valve body II2 adjacent the port I49. The valve body I85 is similar in all respects and contains mechanism identical to the valve bodies I11 and I48, with the exception of the tubular extension I86 and the mechanism contained therein. The tubular extension I86 is provided with a cylindrical bore I81, the outer end of which is closed by a screw plug I88. A piston I89 is axially slidable in the bore I81 and is provided with a piston rod I95 which slidably extends through an aperture in the side wall of the body I85, in the same manner that the piston rod I extends through the side wall of the body I48. A coiled compression spring I9I is positioned in the bore I81 between the piston I89 and the plug I88 and urges the piston rod into the main bore of the body I85.

A port I92 communicates with the bore I81 at the inner end of the piston I89. The valve body I is formed with ports I93, I94, I95 and I96 which are identical with the ports I51, I55, I58 and I55 of the valve body I48. A passage I91 in the valve body I85 is identical with the passage I1I in the valve body I48. A'conduit I98 communicates between the port I19 and the conduit 99, and a check valve I99 is connected between the passage I84 and the conduit I93.

The conduit 62, extending from the gear set I4, communicates with the port I15 of the tubular extension I68, the ports I89 and HM of the valve body I11, and the port I92 of the tubular extension I86 on the valve body I85. The conduit 93 communicates with the port I18 of the valve body I11 and with the port I93 of the valve body I85. The conduit 6| from the gear set communicates with theports 1st and 15s at the valve body, I48, and with the, port I83; of;

the tubular extension ofthe valve body Ill. The.

conduit. 63 from, the. gear set I4; communicates with the port. I 82. of the tubular extension of the. valve Ill. and with the. ports I95 and: IE5. of thevalve body I35; A conduit MI). connects.-

the port I94. ofthe valve body-ififiwith thecon-l duit 99,

tween the passage. I91; and the conduit 2.06, as: The conduit- 60: from the gearset I4. is connected to. a four-way valve 2M: which is,- turn; connectedinto the lineiltas shown. 0011-. 202 with conduit 89.2 A check. valve 204 communicates between the conduit 69 and the conduit I35); and. a checlo and acheck valve 201. isv connected beshown.

duit 203 connects the-valve.

valve.- 205 is connected into the conduit I it between the line I16 and the valve204; as shown. During normal driving in a forward directionthe valve2ii2 is positionedas shown to providecommunicationbetween the conduits BI) and 203; The check valves preferably of restricted capacity.

Operation I32, through the sleeve l I8 and the shuttle valve it] and through the valve I74 to the sump t t via the member I34; out theports MI and conduits I12 (wand 99. The checkvalve il -fl relieves thepressurecreatedby the pumpBIJ; but being of restricted size, will relieve only such pressures as-arecreated as-a result of a predetermined differential between the speeds of the pumps 83 and, i6; WhICh' dififerential is directly proportional to the amount of slippage between the driving and driven elementsofthe couplingd;

Oil is drawnfrom-thesump-84 into the pump- 1-2 throughthe conduits 8|, as, the check valve 87- and the conduit 89; Since the pump Itis not. operating, operation of the pump 'IZWcreates a pressure in=the line 93, and saidpressure is transmitted through the conduit I33; the port I25 thegroove I22, the portIM', the conduit 4-3:), and the passages 21 and 25 to actuate the piston 26 and to-therebylockthe gear set I i-into high gear. The pressure relief valve 94 permits the oil pumped by the pump 'I2 to flowtherethrough from the conduit 93-whenever-the pressure in theconduit 9-3 exceeds approximately 88 pounds, The fluidiiows from the valve 94 through the pressure relief valve 95 which permits said to flow therethrough whenever the pressure thereof exceeds 40 pounds. The fluid flowingthrough the valve 96 returns to the sump S t through theconduits- 98 and 99-. The conduit ill provides a supply of fluid atapproximately- 40 pounds pressure for any desired auxiliary purpose. However; it may beomittedifdesired, to-

gather with the valve 96;

The pressure in the conduit i303 is also transmitted through the conduit I15 and; the port; It!) to the: right hand side of the piston I B'I" inthe; tubular extension- I liil 'of the valve body- Mil.

I73, I14, I97, I99and 201 are.

'I'hispressure holdsthepiston It]; and the rod Ifiiiyin the positionshowninFig. l, in which po,-. sition the spring I518: is compressed and. the rod is out of engagementw-ith the valve member est.

When thedriver to initiate amountot slippage occursin the. coupling 4, and.

the driving element 1 turns rapidly relative to.

the driven element I6, due tothe inability of the coupling to transmit enough power to overcome the inertia oftheautomobile and move it fromia. standstill. in high gear. As a result of thespinr hing-of the element :1 relative to the element It; the pump 8b. pumps a relatively large quantity. of fluid into the conduit 82, While the pump i6; fails to withdraw any therefrom, and a. high pressure is built up in the conduits E2; 991 and i522, said pressure being greater.v than thevalve I'M can relieve. member I3 3 is moved toward the right against the compression of the spring 835.

As the valve member I36 moves toward. the right, the sleeve valve IIB (which had been held. in the position of Fig. 1 by the spring i255 and the shuttle valve I34) is moved to the right against the shoulder I H by the spring 22L aligns the groove I22 with the ports H26 and i21 and aligns the groove I23 with the-ports Imand 529. As a result, the pressure in. the conduits its and i2 and. the groove I22, and: the conduit Bi: is brought into direct communication with: the sump M-through the conduitlld, the port I23, the groove $23, the port- I29 and the conduit 99. Because of this direct communication with the sump it is impossible for pressure to be builtup in the conduit 8| sufficient to cause actuation of the piston Q-in the housing 22.

As the port MI comes into registration with the port I38 of the valve body i I 2, fluid-under pressurefrom the conduit 82 flows from theshuttle valve ports MI I and I38 and lifts the piston !52. As the piston I52 is lifted, the inner end of the-piston rod I snaps into the groove I59 and holds the valve MI in its raisedor outer most position. The peripheral groove Ittcf the. valve member IiiI registers with the ports Iii'i and 553 of the valve body Mil when the member Iii i is in its raised position. then flows from the conduit 93 through theconduit I-l5, the port I51, the groove i5 5, the port E58 andthe conduit 6! to the actuating mechanism of the brake band 32. Since the piston 23 released the friction plate 3} when the pressure in the line I30 was relieved, the driven shaft i2 is no longer locked to the clutch wheel 23 and continuesto rotate while the clutch wheel is held stationary bythe brake band 3 2. The transmission is now in third gear. If the slippage between thedriving and the driven elements of the coupling t is so great thatthe pressure in the conduit 82 resulting therefrom exceeds the amount which can be counterbalanced by the spring I35, then "the shuttle valve member H lwill move to the right to bring the port It} into registration with the port I39.

The fluid pressure within the shuttle valve I34 raises the piston in the valve body Ill in the same manner that the piston I52 was raised during the previous step. Pressure from the conduit 93 now flows through the ports lit and I and through the conduit 52 to the actuating mechanism for the brake band 35. Simultaneously, pressure; from the line 52 also enters the cylinder bores IE2 and Ill? to hold the pistonrods depresses the accelerator we, motion of the automobile, a great.

As a result, the shuttle valve I16 is relieved through the ports 12B and Fluid under pressure I65 and I90 retracted, as shown in Fig. 1. Retraction of the piston rod I85 releases the valve member I! and permits said member to move downwardly under the urging of the spring 53 thereabove. The fluid from the cylinder I51; below the piston I52 bleeds back to the sump thrOugh the port I38, the groove I42 (which is in registration therewith), and the conduit 99. As the valve member IiiI moves downwardly, pressure in the conduit BI and to the port I83 oi the valve body ii? is relieved, thereby releasing the brake band 32 and permitting the piston rod within the valve body ill to lock the valve therein in raised position. The gear set 54 is now in second gear.

If the between the driving and driven elements of the coupling 4 is still so great that the pressure from the conduit 82 is greater than that which can be counterbalanced by the spring I35, the shuttle valve member I34 moves still farther to the right until the projection I35 thereon abuts the screw plug II4. In this position the port I i-I registers with the port I40. Fluid under pressure flowing through the ports I40 and iii lifts the valve member and the piston in the valve body I85 and causes fluid under pressure to flow from the conduit 53 through the ports I83 and I95 into the conduit 83. Fluid pressure in the conduit 63 enters the port iii? of the valve body ill and retracts the piston and piston rod therein from looking position, thereby permitting the valve member within the valve body I'I'i to return to the position of the valve member I5I shown in Fig. 1. As this occurs, pressure from the line 93 is cut off from the conduit 62, as is the pressure to the ports HI) and I92. The brake band 35 is thereby released, and the pressure in the conduit 63 actuates the brake band 46, to hold the ring gear 43 stationary. As

the pressure at the port I92 is relieved, the piston rod I90 snaps to the right to lock the valve member in the body I85 in raised position. The gear set I4 is now in low gear.

In low gear the gear set I4 transmits the greatest amount of power to the driven shaft 38, and the automobile, if it has not already done so, begins to move forward. The slippage between the driving and driven elements of the coupling 4 decreases as the automobile picks up speed, and accordingly the speed of the pump I6 begins to approach the speed of the pump 30. This decreases the pressure in the conduit 82 and in the shuttle valve I34, and the pressure of the spring I355 eventually overcomes this pressure to move the shuttle valve member I34 to the left sufficient to bring the port MI into registration with the port I39. This raises the valve member in the valve ill and lowers the valve member in the valve itt to thereby cause release of the brake band 46 and engagement of the brake band 35 thus shifting the gear set 14 into second gear. Any slight increase in the slippage in the coupling 4 resulting in a corresponding increase in pressure in the conduit 82 is relieved by the check valve I99.

As the car accelerates in second gear the speed of the driven element of the coupling continues to approach the speed of the driving element l, and accordingly the speed of the pump '16 continues to approach the speed or" the pump 8t. This further lowers the pressure in the conduit 82, and when the pressure within the shuttle valve I34 is overcome by the pressure of the spring l35, said spring moves the shuttle valve 34 to the left to bring the port I4I into registration with the port I38. This raises the valve member I5I and lowers the valve member in the valve Ill to thereby cause engagement of the brake band 32 and release of the brake band 35. The gear set 54 is now in third gear, and any slight increase in the pressure in the conduit 32, resulting from increased slippage due to the upshift, is relieved by the check valve H3.

The automobile continues to accelerate in third gear, and the pump 16 accordingly continues to approach the speed of the pump 80. The pressure in the conduit 82 and in the shuttle valve member I34 continues to decrease, and when this pressure is overcome by the spring I35, the shuttle valve member is moved to the left to the position of Fig. 1 thereby releasing the brake band 32 and causing the piston 23 to lock the friction plate 3| to the flange 24, to shift the gear set 54 in high gear.

Simultaneously, the communication between the conduit 85 and the conduit 99 through the groove i23 of the sleeve slight increase in slippage between the driving and driven elements of the coupling 4 resulting from the upshift to high gear, and causing a corresponding increase in pressure in the conduit 82 is relieved by the check valve I14.

As the car accelerates in high gear the speed of the driven member I6 gradually approaches the speed of the driving member I until the slippage therebetween is at a minimum and the efiiciency of the coupling is at a maximum. As an example, this point may be reached in certain couplings when the speed of the driven member I6 is approximately 85% of the speed of the driving member i regardless of what the actual speed of the elements is. The size of the pump 12 is such that when the efficiency of the coupling 4 very closely approaches its maximum, the amount of oil pumped into the conduit 8I by the pump I6 is greater than the amount of oil drawn from said conduit by the pump 72. This causes a building up of pressure in said conduit, and this pressure is transmitted through the conduit 68 and the passages 61 and 66 to the piston 9 which in turn locks the friction plate I5 to the flange I I. When the coupling 4 is so engaged, the driving element I is fixedly connected to the driven element, thereby eliminating all slippage and providing a direct drive between the shafts 5 and I2. The elements of the coupling 4 are automatically locked up in the manner described at any speed at which the coupling approaches a predetermined state of near minimum slippage. The improved lock-up mechanism makes it possible for the automobile to be pushed for starting purposes, since the coupling 4 is automatically locked up when the driven element I6 tends to drive the driving element '1, this being true because in such a case the speed of the pump I6 would exceed that of the pump I2, and would therefore create the pressure in the conduit 8| necessary for the locking-up operation.

Once the coupling 4 is locked up, it normally remains locked up until the speed of the automobile decelerates to slightly above idling speed. At this speed the normally open bleeder valve 88 of predetermined limited capacity bleeds off to the sump 84 the excess fluid pumped into the line 8I by the pump I6, thereby relieving the piston 9 and unlocking the coupling 4.

There are times, however, when it is desired to have increased power over and above that available in high gear. the power needed to pass another carorthe addi-v IIS is shut cit. Any- An example of this isto...thereby get increased; power, it is only necessary; to. depress the accelerator IIlIJ to. the floor, thereby depressing the valve stem I 02 I Ill.- and movingthevalve lilfiqdownwardlyagainst the compression of the with. the ports. IM and I05. 'Qpen-ing of the valve, Illl. in this'manner permits the excess fluid the. conduit ill to bleed-through. the conduit 85, the conduit I 09, the valve Illl the conduits H0, 98 and .99backto thesumpfl l. Bleeding of. the: excess fluid. from, the conduit. I-, of course, causes the. pressure in said lineto drop, thereby releasing the friction, plate I5 from locking engagement by'the annular piston 9. and disengaging the. driving element of the coupling 4. from the. driven element thereof.

Accelerationof. the engine due to depression of the; accelerator I00 increases the slippage between, of the coupling, and, in.

the; released elements;

themanner previously described, the transmission gear set 54 is automatically shifted to a.

lower, gear in accordance with slippage in the coupling. be depressed all. the way down only. long enough tocause disengagement ofthe coupling ele ments. It may then beraised out of depressing contact with the. valve H]! to again close said the amount of valve.= When the increased power is no longer.

needed. or. thedesired speed is attained, and the accelerator I 00. is raised to normal driving position, the .efiiciency of the coupling again increases to,,approach its maximum: When the predetermined condition of near minimum slippage is attained, the coupling, automatically becomes locked up. as before.

To accomplishv movement of the, automobile in reverse, it1is only necessary to turn the. valve 202 90 in a. clockwise direction so that it provides communication between the outletof the pump- I2and the conduit 60.

theright of the-valve Ziiildsbled back to the sump 8.4 through the conduit 2H3.

It,.is. apparent that the improved transmission. M, into the par-. maximum effiautomatically shifts the. gear set. ticular step, which will. result in. a ciency (minimum slip) of. the coupling. For example, if the automobile down grade wherein the power necessaryto move the automobile from. standstill is lessthan that which, would be necessary if the automobile was- 012: a level-grade, the. transmission intov low ear if: the car can be second or thirdgearwithout excessive slippage in the coupling. This differs from. conventional. automatic transmissions wherein the gear shift.- ing depends entirely upon the speed of the v hicle and not upon the slippage in the coupling. Regardless of what step. the gear set I l. may he. in,. the transmission. will. automatically adiust itself to1 changing load conditions by shifting into other steps, whether higher or lower, to maintain maximum efficiency (minimum coupling slips page)... This, possible dueto the fact. that, the

changing. load conditions, are. in tantly reflected of the valve spring IE8 to bring. the passage; I0! of. the valve into. communication The accelerator need In this position pressure fromthe pumplli causesactuation of. the pistons.

is starting on a slight.

may shiftthe gear set Mdntosecondor. thirdgear rather; than moved. in eitherw l to. prevent back:

electrostatic coupling. cite mechan al nerj transmissionis designed sothattheshuttle valve, I

I 341 always seeksthehighest gear ratio which the couplingcan pull withoutexcessiveslippage;

The. improved lockrup v feature of the-invention; greatly. increases the, efliciency transmission over: those having lock-up, mechanisms responsive entirely to speed. In additiom the lock-up mechanism of the invention permits;v an automobile to. travel; at. low speeds .with. the; couplingthereof, locked up. This; permits safedriving bothronslipperyroadsand. when traveling downhill, by'permittingthecoupling to; be locked,- up atsuch times.

Theautomatic shifting feature of the improved; transmission which maintains the coupling iny a; condition of least; possible slippage regardless; of the speed of the vehicleqand the. load, isanim-h movement over conventional, automatic trans missions which shiftjnaccordance: with the; speed; of the vehicle, because in the latter the motoriirequently overdrives andcausesexcessive slippage. This slippage is very wasteful and causes heating up of the coupling as well as excessive gasoline consumption. A further advantageous feature; of; the improved automatic transmission is the fact that no manual control whatever is required to shift the gear set It from one forward step to an-. other regardless of the step into whichthe gear set is to be shifted for maximum eificiency.

As previously pointed out, the gear set I4 in v the improved transmission is engaged in high gear; whenever the engine driving said transmission is, idling. This is different fromv certain convert-- tional automatic transmissions which have theiiv gear sets engaged in a lower gear atsuch times. The latter type of transmission tends to cause the. vehicle to creep when the vehicle is at a stand-. still with its engine idling, suchas whenthe ve-..- hicle-is stoppedfor a stop sign or the like. To overcome the creeping it.is necessary to apply the brake. The improved transmission avoids all. tendency to causecreepingwhen idling ata standstill by.- havingthegear set engagedin high gear at,such times and thereby taking-advantage-of. the fact thatthe, fluid couplingin. the improved nsm si n doesnt. transmit no h orqueats idling speed to move th e,.vehic1e -f10m;astandstilL when the gear set is. engaged in high gear.

As an additional feature of theimproved trans: mission, the ones-way. brake provided. by the camsv strand the bearings 2 I is-effectiveas a hill holder sliding of the vehicle when stopped: on. an up-hill grade. The parts2Il and.- 2i. provide a one-wayfbrake. which prevents rev rs rotation: of. he h ft I2. the housing fthe. planetary gearset. I lbeingnon-wtatable, since the shaft 52 is preventedfrom.rotating ina"re... r e irectiom h t M sp v hted;.from rotating in a reverse: dnection at. any time the gear. set. It. has a. forward. speed train engaged. This; provides anautomatic hill holding. meanswhioh prevents the car from travelling backwardly at. any time aforwardgear train. is. enga ed. This... eiiininatesthe necessity ofusing the brakeor the engine. to .holdthe vehicle at such times.

. Whilethe invention has. been. shown and. described as applied. to an. automatic transmission having embodied. therein a. fluid coupling, any. suitable, power transmitting mechanism having a slip characteristic may e used, such, asa dr toroue. converter; an elect c. s ip oupli type power transmitting mechanism, all of whic of the present;

are well known in the power transmitting art. An example of an electrostatic coupling is one wherein particles of dielectric material are suspended in an insulating fluid contained between closely spaced rotatable metallic plates which form the driving and driven elements of the coupling. High voltage applied to the plates causes an increase in viscosity of the fluid and transmission of torque from one rotating plate to the other. A mechanical inertia type transmission is a device by means of which the torque ratio can be continuously varied by mechanical means, usually by means of roller ratchets or equivalent devices. In certain types power is transmitted by imparting an oscillating motion to one race or ring of a roller ratchet, and the torque ratio is controlled varying the amplitude of the oscillations.

Various other changes and modifications may be made without departing from the spirit of the invention, and all. of such changes are contemplated as may come within the scope of the claims.

What is claimed as the invention is:

l. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element; a pump driven by said driven element; a pump of predetermined smaller size driven by said driving element; means for supplying fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluidsupplied pump to the inlet of the other of said pumps and to said fluid pressure actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined fluid pressure condition in said conduit mans in response to which the element connecting mechanism directly connects said driving and driven elements.

2. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of predetermined smaller size driven by said driving element; means for supplying fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluidsupplied pump to the inlet of the other of said pumps and to said fluid pressure actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined fluid pressure condition in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements.

' 3. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of a predetermined smaller size driven by said driving element; means for supplying hydraulic fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps and to said fluid pressure actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined fluid pressure condition in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements.

4. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and hydraulically actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of smaller size driven by said driving element; means for supplying hydraulic fluid to the inlet of said driven element pump; and conduit means connecting the outlet of said driven element pump to the inlet of said driving element pump and to said hydraulically actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined hydraulic pressure in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements.

5. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and hydraulically actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of predetermined smaller size driven by said driving element; means for supplying hydraulic fluid to the inlet of said driven element pump; conduit means connecting the outlet of said driven element pump to the inlet of said driving element pump and to said hydraulically actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined hydraulic pressure in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements; and a normally open bleeder valve of restricted capacity in said conduit means.

6. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and hydraulically actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of predetermined smaller size driven by said driving element; a source of hydraulic fluid; means for supplying hydraulic fluid from said source to the inlet of said driven element pump; conduit means connecting the outlet of said driven element pump to the inlet of said driving element pump and to said hydraulically actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined hydraulic pressure in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements; an inlet check valve communicating between said conduit means and said source of hydraulic fiuid; and a normally open bleeder valve of restricted capacity in said conduit means.

'I. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a variable speed transmission driven by said driven element; a driven shaft driven by said transmission; fluid pressure actuated shifting mechanism connected to said transmission for varying the speed of said driven shaft relative to that of said driven element; a pump driven by said driving element; a pump driven by said driven element; means for supplying fluid to the inlet of one of said pumps; and conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps and to said fluid pressure actuated shifting mechanism, whereby rotation of the driving element at a predetermined speed relative to the driven element causes a fluid pressure condition in said conduit means.

8. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element; a variable speed transmission driven by said driven element; a driven shaft driven by said transmission; fluid pressure actuated shifting mechanism connected to said transmission for varying the speed of said driven shaft relative to that of the driving element; a first positive displacement pump driven by said driving element; a second positive displacement pump driven by said driven element; means for supplying fluid to the inlet of said first pump; first conduit means connecting the outlet of the first pump to the inlet of the second pump and to said fluid pressure actuated shifting mechanism; a third positive displacement pump driven by said driving element; and second conduit means connecting the outlet of said second pump to the inlet of said third pump and to said fluid pressure actuated element connecting mechanism.

9. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element; a variable speed transmission driven by said driven element; a driven shaft driven by said transmission; fluid pressure actuated shifting mechanism connected to said transmission for varying the speed of said driven shaft relative to that of the driving element; a first positive displacement pump driven by said driving element; a second positive displacement pump driven by said driven element; means for supplying fluid to the inlet of said first pump; first conduit means connecting the outlet of the first pump to the inlet of the second pump and to said fluid pressure actuated shifting mechanism; a third positive displacement pump driven by said driving element; second conduit means connecting the outlet of said second pump to the inlet of said third pump and to said fiuid pressure actuated element connecting means; and a normally closed bleeder valve in said second conduit means, said valve also being connected to said first conduit means and being responsive to a predetermined pressure therein to open and bleed said second conduit means and prevent the building up of substantial pressures therein, thereby rendering the element connecting mechanism inoperative.

10. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element; a variable speed transmission driven by said driven element; a driven shaft driven by said transmission; fluid pressure actuated shifting mechanism connected to said transmission for varying the speed of said driven shaft relative to that of the driving element; a first positive displacement pump driven by said driving element; a second positive displacement pump driven by said driven element; means for supplying flui to the inlet of said first pump; first conduit means connecting the outlet of the first pump to the inlet of the second pump and to said fluid pressure actuated shifting mechanism; a third positive displacement pump driven by said driving element; second conduit means connecting the outlet of said second pump to the inlet of said third pump and to said fluid pressure actuated element connecting means; a normally released accelator; and a normally closed accelerator operated bleeder valve in said second conduit means, said valve being responsive to depression of the accelerator a predetermined amount to bleed said second conduit means and reduce the pressure therein and to thereby release the element connecting mechanism.

11. In combination: a power transmitting mechanism having a. rotary driving element adapted to be driven by a source of power, a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element; a variable speed transmission driven by said driven element; a driven shaft driven by said transmission; fluid pressure actuated shifting mechanism connected to said transmission for varying the speed of said driven shaft relative to that of the driving element; a first positive displacement driving element; a second pump driven by said driven supplying fluid to the inlet first conduit means connectpcsitive displacement element; means for connecting means.

12. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary element to said driven element; transmission driven by said driven element; a driven shaft driven by said transmission; fluid pressure actuated shifting mechanism connected to said transmission for said driven shaft relative to that of the driving element;

ment; means for supplying fluid to the inlet of said first pump; first conduit means connecting the outlet of the first pump to the inlet of the second pump and to said fluid pressure actuated shifting mechanism; bleeder valve means normally communicating with said first conduit means; an inlet check valve communicating between said first conduit means and a source of hydraulic fluid; a pressure relief valve in said first conduit means; a third pump driven by said driving element; a second conduit means convalve in said conduit means,

nectirig the outlet of said second pump to the inlet of said third pump and to said fluid pressure actuated element connecting means; a pressure relief valve in said second conduit means; and an inlet check valve communicating between said second conduit means and a source or hydraulic fluid.

13. In combination: a power transmitting mechanism having a rotary driving element and a rotary driven element; a positive displacement pump driven by said driving element; a positive displacement pump driven by said driven element; means for supplying fluid to the inlet of said driving element pump; conduit means conmeeting the outlet of the driving element pump to the inlet of the driven element pump; a planeta ry 'transmission driven by said driven element and having a plurality of planetary trains; an hydraulically actuated engaging mechanism for eachofzsaid trains, each of said mechanisms having a conduit leading thereto; a source of fluid under pressure; and a distribution valve connected to said source of fluid under pressure and to said train engaging mechanism conduits, said valve also being connected to said conduit means and being responsive to a predetermined pressure in said conduit means to deliver fluid under pressure from said source to a predetermined train engaging mechanism.

14. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element; a pump driven by said driven element; a pump driven by said driving element; means for supplying fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps and to said fluid pressure actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined fluid pressure condition in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements; a normally released accelerator; and a normally closed accelerator operated bleeder valve in said conduit means, said valve being responsive to a predetermined movement of the accelerator to vent said conduit means and relieve the pressure condition therein to thereby release the element connecting mechanism,

15. In combination; a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power,-a rotary driven element, and fluid pressure actuated mechanism for directly connecting said driving element to said driven element a positive displacement. pump driven by said driven-element; a positive displacement pump driven by said driving element; means for supplying hydraulic fluid to the inlet of one of said pumps; conduitmeans connecting the outlet of said last mentioned pump to the inlet of the other of said pumps and to said fluid pressureactuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined fluid pressure condition in said conduit means in response to which the elementconnecting mecha nism directly connects said driving and driven elements; a normally released accelerator; and a normally closed accelerator operated bleeder said valve being responsive to a predetermined movement of the accelerator to vent said conduit means and relieve the pressure condition therein to thereby release theelement connecting mechanism.

16. in combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and hydraulically actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of predetermined smaller size driven by said driving element; a source of hydraulic fluid; means for supplying hydraulic fluid from said source to the inlet of said driven element pump; conduit means connecting the outlet of said driven element pump to the inlet of said driving element pump and to said hydraulically actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined hydraulic pressure in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements; a pressure relief valve communicating with said conduit means; and an inlet check valve communicating between said conduit means and said source of hydraulic fluid.

17-. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and hydraulically actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of predetermined small size driven by said driving element; a source or hydraulic fluid; means for supplying hydraulic fluid from said source to the inlet of said driven element pump; conduit means connecting the outlet of said driven element pump to the inlet of said driving element pump and. to said hydraulically actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined hydraulic pressure in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements; a pressure relief valve in said conduit means; an inlet check valve communicating between said conduit means and said source of hydraulic fluid; and a normally open bleeder valve of restricted capacity in said conduit means.

18. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and hydraulically actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of predetermined smaller size driven by said driving element; a source of hydraulic fluid; means for supplying hydraulic fluid from said source to the inlet of said driven element pump; conduit means connecting the outlet of said driven element pump to the inlet of said driving element pump and to said hydraulically actuated means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes a predetermined hydraulic pressure in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements; a pressure relief valve in said conduit means; and an inlet check valve communicating speed ratios; a source garage? between said conduit means and said source of hydraulic fluid.

19. In combination: a transmission having a driving shaft and a driven shaft, said transmission being shiftable to provide a plurality of speed ratios between said driving and driven shafts; a separate fluid pressure actuated transmission shifting mechanism for each of said speed ratios; a source of fluid under pressure; a variable pressure conduit means; a distribution valve connected to said conduit means, said valve having a separate auxiliary valve connected to each of said shifting mechanisms and to said source of fluid under pressure, said auxiliary valves being normally closed and each of the later being actuatable to open position wherein they deliver fluid under pressure from said source to the shifting mechanism connected to said auxiliary valve, said distribution valve also having a movable member for successively actuating said auxiliary valves in response to predetermined pressures in said conduit means; and releasable locking mechanism connected to said auxiliary valves and responsive to actuation of one of said valves to hold the latter in open position until another auxiliary valve is actuated by said movable member.

20. In combination: a transmission having a driving shaft and a driven shaft, said transmission being shiftable to provide a plurality of speed ratios between said driving and driven shafts; a separate fluid pressure actuated transmission shifting mechanism for each of said of fluid under pressure; a variable pressure conduit means; and a distribution valve connected to said conduit means, said valve having a separate pressure responsive auxiliary valve connected to each of said shifting mechanisms and to said source of fluid under pressure, said auxiliary valves being normally closed and each of the latter being actuatable to open position wherein it delivers fluid under pressure from said source to the shifting mechanism connected to said auxiliary valve, said distribution valve also having a movable ported member which is successively registrable with said auxiliary valves in response to predetermined pressures in said conduit means to deliver fluid under pressure from said conduit means to the auxiliary valve with which the distribution member is in register to actuate said auxiliary valve. I

21. In combination: a transmission having a driving shaft and a driven shaft, said transmission being shiitable to provide a plurality of speed ratios between said driving and driven shafts; a separate fluid pressure actuated transmission shifting mechanism for each of said speed ratios; a source of fluid under pressure; a variable pressure conduit means; a distribution valve connected to said conduit means, said valve having a separate pressure responsive auxiliary valve connected to each of said shifting mechanisms and to said source of fluid under pressure, said auxiliary valves being normally closed and each of the latter being actutable to open position wherein it delivers fluid under pressure from said source to the shifting mechanism connected to said auxiliary valve, said distribution valve having a movable ported distribution member which is successively registrable with said auxiliary valves in response to predetermined pressures in said conduit means to deliver fluid under pressure from said conduit means to the "auxiliaryvalvewith which the distribution memher is in register to actuate said auxiliary valve; and releasable locking mechanism connected to said auxiliary valves and responsive to actuation of one of said valves to hold the latter in open position until another auxiliary valve is actuated.

22. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a transmission driven by said driven element and having a driven shaft, said transmission being shiftable to provide a plurality of speed ratios between said driven shaft and said driven element; a separate fluid pressure actuated transmission shifting mechanism for each of said speed ratios; a source of fluid under pressure; a pump driven by said driving element; a pump driven by said driven element; means for supplying fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps; and a distribution valve connected to said source of fluid under pressure and to said shifting mechanisms, said valve also being connected to said conduit means and being responsive to a predetermined pressure condition in said conduit means to deliver fluid under pressure from said source to a predetermined shifting mechanism.

23. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a transmission driven by said driven element and having a driven shaft, said transmission being shiftable to provide a plurality of speed ratios between said driven shaft and said driven element; a separate fluid pressure actuated transmission shifting mechanism for each of said speed ratios; a source of fluid under pressure; a pump driven by said driving element; a pump driven by said driven element; means for supplying fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps; and a distribution valve connected to said source of fluid under pressure and to said shifting mechanisms, said valve also being connected to said conduit means, and said valve normally being in a position to deliver fluid under pressure from said source to the shifting mechanism for effecting the highest of said speed ratios and being responsive to a predetermined pressure condition in said conduit means to deliver fluid under pressure from said source to a predetermined shifting mechanism.

24. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a transmission driven by said driven element and having a driven shaft, said transmission being shiftable to provide a plurality of speed ratios between said driven shaft and said driven element; a separate fluid pressure actuated transmission shifting mechanism for each of said speed ratios; a source of fluid under pressure; a positive displacement pump driven by said driving element; a positive displacement pump driven by said driven element; means for supplying hydraulic fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps; and a distribution valve connected to said source of fluid under pressure and to said shifting mechanisms, said valve also being connected to said conduit means and being responsive to a. predetermined pressure condition in said conduit means to deliver fluid under pressure from said source to a predetermined shifting mechanism.

25., In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a transmission driven by said driven element and having a driven shaft, said transmission being shiftable to provide 'a plurality of speed ratios between said driven shaft and said driven element; a separate fluid pressure actuated transmission shifting mechanism for each of said speed ratios; a source of fluid under pressure; a positive displacement pump driven by said driving element; a positive displacement pump driven by said driven element; means for supplying hydraulic fluid to. the inlet of said driving element pump; conduit means connecting the outlet of said driving element pump to the inlet of said driven element pump; and a distribution valve connected to said source of fluid under pressure and to said shifting mechanisms, said valve also being connected. to said conduit means and being responsive to a predetermined pressure in said conduit means to deliver fluid under pressure: from said source to a predetermined shifting mechanism.

26. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a transmission driven by said driven element and having a driven shaft, said transmission being shiftable to provide a plurality of speed ratios between said driven shaft and said driven element; a separate fluid. pressure actuated transmission shifting mechanism for each of said speed ratios; a source of fluid under pressure; a pump driven by said driving element; a, pump dr'ven by said driven element; means for supplying fluid to the inlet of one oi said pumps; conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps; and a distribution valve connected to said conduit means, said valvahaving a separate auxiliary valve connected to each.

of said shifting mechanisms and: to said source of fluidunder pressure, said auxiliary valves being normally closed and each of the latter being actuatable to open positionv wherein they deliver fluid under pressure from said source to.

the shifting mechanism connected to said auxiliary valve, said distribution valve also: having a movable member for successively actuating said auxiliary valvesv in response to predetermined pressure conditions in said conduit means.

27. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven, element; a transmission driven by said driven element said transmission being shiftable to provide a plurality of speed ratios between said driven shaft and said driven element; a separate fluid pressure actuated transmission shifting mechanism for each of said speed ratios; a source of; fluid.

under pressure; a pump driven by said driving element; a pump driven by said driven element; means for supplying fluid to the inlet. of oneof said pumps; conduit means connecting theoutlet of said fluid-supplied pump tovthe inlet of the other of said pumps; a distribution valve connected to, saidconduitmeans; saidvalve having a separate auxiliary valve connected to each of said shifting mechanisms and. to said source 01 fluid-L under pressure, .said auxiliary-valves; be

and having a driven shaft,

iii

under pressure; a pump ing normally closed and each of the latter being actuatable to open position wherein they deliver fluid under pressure from said source to the shifting mechanism connected to said auxiliary valve, said distribution valve also having a movable member for successively actuating said auxiliary valves in response to predetermined pressure conditions in said conduit means, and releasable locking mechanism connected to said auxiliary valves and responsive to actuation of one of said valves to hold the latter in open position. until another auxiliary valve is actuated.

28. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a transmission driven by said, driven element and having 'a driven shaft, said transmission being. shiitable to provide a plurality of speed ratios between said driven element and said driven shaft; a separate: fluid pressure actuated trans-mission shifting. mechanism for each of. said. speed, ratios; a source of fluid under pressure; a pump driven by said drivin element; a pump driven by said driven element;

means for supplying fluid to the. inlet of; one of said pumps"; conduit. means. connecting the outlet of said fluid-supplied pump to the inlet of the other of said: pumps; and redistribution valve connected to said conduit means, said: valve" having a separate auxiliary valve connected to 'e'ach of said shifting mechanisms and ta said source of fluid? under pressure, said. auxiliary valves being normally closed and each ofrthe latter: being actuatable to open position whereinthey deliver fluid under pressure from said source to the: shifting mechanism connected to-saidr. auxiliary val've, said distribution valve also having a movable member for successively actuating: said auxiliary valvesin response to predetermined pressure conditions in: said conduit means, said" movable membernormally being in a position to actuate'the auxiliary valve connected to the shifting mechani'sm providing the highest speed ratio of said transmission.

291. In combination:- a power transmitting mechanism having a rotary driving element adapted. tobe driven by'a source of power andia rotary driven element; a transmission driven by said driven element and having a driven shaft,

said transmission being shiftable to: provide a plurality 'ofspeed'ratios between said driven shaft and said driven element; a separate fluid p'r'essure actuated transmission shifting mechanism for-"each of said speed ratios; a source of'fluid driven by said driving elementy a pumpdriven by'saiddriven element; means for supplying fluidto theinlet of one'of said pumps; conduit means connecting the outlet of said fluid-suppliedpump to theinlet' ofthe other of said pumps; and a distribution valve connected't'o said'conduit' means, said valve having a separate auxiliaryv valveconnecte'd to each of. said shifting mechanisms and to saidsource of fluidunder pressure, said auxiliary valves beingnormally closed-and-each of thelatter being actuatable. to'open position wherein. they deliver fluid-underpressure fromsaid source to the shifting; mechanism connected to said auxiliary valve, said, distribution valve also having a. movable ported member whichissuccessively registrable with said :aux-iliaryvalves in response topredetermined. pressure: conditions vin said conduitmeans to connect said c'onduit meanswithmhe; auxiliary valve-with-wlncn thamovablamembec is-in' register and thereby cause actuation of said auxiliary valve.

30. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a transmission driven by said driven element and having a driven shaft, said transmission being shiftable to provide a plurality of speed ratios between said driven shaft and said driven element; a separate fluid pressure actuated transmission shifting mechanism for each of said speed ratios; a source of fluid under pressure; a pump driven by said driving element; a pump driven by said driven element; means for supplying fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps; a distribution valve connected to said conduit means, said valve having a separate auxiliary valve connected to each of said shifting mechanisms and to said source of fluid under pressure, said auxiliary valves being normally closed and each of the latter being actuatable to open position wherein they deliver fluid under pressure from said source to the shifting mechanism connected to said auxiliary valve, said distribution valve also having a movable ported member which is successively registrable with said auxiliary valves in response to predetermined pressure conditions in said conduit means to connect said conduit means with the auxiliary valve with which the movable member is in register and thereby cause actuation of said auxiliary valve, and releasable locking mechanism connected to said auxiliary valve and responsive to actuation of one of said valves to hold the latter in open position until another auxiliary valve is actuated.

31. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a variable speed transmission driven by said driven element; a driven shaft driven by said transmission; fluid pressure actuated shifting mechanism connected to said transmission for varying the speed of said driven shaft relative to that of said driven element, said shifting mechanism normally effecting the highest speed ratio between said driven element and said driven shaft; a pump driven by said driving element; a pump driven by said driven element; means for supplying fluid to the inlet of one of said pumps; and conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps and to said fluid actuated shifting mechanism, whereby rotation of the driving element at a predetermined speed relative to the driven element causes a predetermined fluid pressure condition in said conduit means in response to which said shifting mechanism effects a predetermined relationship between the speed of the driven shaft and that of the driven element.

32. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and hydraulically actuated mechanism for directly connecting said driving element to said driven element; a positive displacement pump driven by said driven element; a positive displacement pump of predetermined smaller size driven by said driving element; means for supplying hydraulic fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluid-supplied nects said driving and driven elements; and a normally open bleeder valve of restricted capacity in said conduit means. i

33. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power and a rotary driven element; a transmission driven by said driven element and having a driven sure; a distribution valve connected to said second source and to said shifting mechanisms and responsive to a predetermined fluid pressure condition in said valve to deliver fluid under pressure from said second source to a predetermined shifting mechanism, said valve normally being in a position to deliver fluid under pressure from said second source to the shifting mechanism for effecting the highest of said speed ratios; and pump means connected to said first source and to said distribution valve and driven by said driving and driven elements in a manner to create said predetermined pressure condition in said valve in response to relative rotation of said driving and driven elements.

34. In combination: a power transmitting mechanism having a rotary driving element adapted to be driven by a source of power, a rotary driven element, and mechanism responsive to a predetermined fluid pressure condition therein for directly connecting said driving element to said driven element; a pump driven by said driven element; a pump dr1ven by said driving element; means for supplying fluid to the inlet of one of said pumps; conduit means connecting the outlet of said fluid-supplied pump to the inlet of the other of said pumps and to said fluid pressure actuated element connecting means, whereby rotation of the driven element at a predetermined speed relative to the driving element causes said predetermined fluid pressure condition in said conduit means in response to which the element connecting mechanism directly connects said driving and driven elements.

ALBERT P. SCHNEIDER.

References Cited in the file of this patent UNITED STATES PATENTS 

